Pneumatic spinning frame drive regulator



J ly 25, 196 R. D. JOY 3,332,224

PNEUMATIC SPINNING FRAME DRIVE REGULATOR Filed Nov. 17, 1964 6 Sheets-Sheet 1 INVENTOR iiw ma/va I Jar BYZ:

ATTORNEYS July 25, 1967 R 11 JOY PNEUMATIC SPINNING FRAME DRIVE REGULATOR Filed Nov 17, 1964 6 Sheets-Sheet 2 I w mm INVENTOR lEQYMd/VJJ J) wa mm ATTORNEYS RID. JOY

July 25, 1967 PNEUMATIC SPINNING FRAME DRIVE REGULATOR Filed Nov. 17, 1964 6 Sheets-Sheet A, w v

INVENTOR ,EQYMa/VD J. Jr

BY ATTORNEYS July 25, 196 R. D. JOY 3,332,224

PNEUMATIC SPINNING FRAME DRIVE REGULATOR Filed Nov. 17, 1964 6 Sheets-Sheet 4 7/& 7% Wax 5 3 4 3f Z2 p r74 Aw 3 1M 1 INVENTOR ORNEYS July 25, 1967 R. D. JOY 3,332,224

PNEUMATIC SPINNING FRAME DRIVE REGULATOR Filed Nov. 17, 1964 6 Sheets-Sheet 5 J Z7 *m ig 0 j; 8 INVENTOR ATTORNEY5 July 25, 1967 R JOY 3,332,224

PNEUMATIC SPINNING FRAME DRIVE REGULATOR Filed Nov. 17, 1964 6 Sheets-Sheet 6 INVENTOR ATTOR NEYS United States Patent 3,332,224 PNEUMATIC SPINNING FRAME DRIVE REGULATOR Raymond 1). Joy, Mecklenburg County, Va., assignor to Burlington Industries, Inc., Greensboro, N.C., a corporation of Delaware Filed Nov. 17, 1964, Ser. No. 411,850 18 Claims. (CI. 57-95) The present invention relates to an improved drive regulator mechanism for controlling and changing a variable speed drive of winding machines, such as spinning frames, and more particularly, to a pneumatic system and mechanism for varying to optimum conditions the speed of a winding machine from an empty bobbin to a full bobbin and within the build of the bobbin. The drive regulator mechanism of the present invention is disclosed in association with a spinning frame or machine, although it is to be understood that the present invention may be readily adapted to other applications wherein it is desired to regulate a condition dependent on a predetermined program and/or the immediate magnitude of the condition without a lag.

In a conventional spinning machine of the type having rotating spindles for receiving the bobbins and a reciprocating and traversing ring rail, it is well known that the friction and tension on the yarn is greater at small diameters of the package due to the relative sharp angle of the yarn between the traveler and the bobbin. As the diameter of the package increases and as the build of the package increases, the tension and friction on the yarn lessens. It is, therefore, a desired operating condition to increase the speed of the spinning frame as the package builds on the bobbin and the tension and friction decrease on the yarn so as to increase the output of the spinning frame.

Heret-ofore, various speed change or control mechanisms or arrangements have been utilized for varying the speed of a spinning machine during each reciprocation of the ring rail and during each movement of the ring rail to a new position of traverse. The prior art mechanisms included providing a Reeves type drive between a constant speed shaft of a constant speed motor and the main shaft of the spinning frame, the adjustable pulley of the Reeves drive being controlled pneumatically. Such prior systems are disclosed in Joseph R. Lons US. Patent Nos. 2,803,107 issued Aug. 20, 1957; 2,918,779 issued Dec. 29, 1959; and 3,015,204 issued June 2, 1962. The present invention is an improvement over such prior disclosures and includes means of programming and accurately sensing a condition such as programming the build of a bobbin directly from the reciprocation of the ring rail and/or the position of traverse of the ring rail and regulating the speed of the spinning frame therefrom dependent upon the program initiated to control the starting or minimum speed of the spinning frame, the maximum speed of the spinning frame, the rate of increase of speed from the minimum speed to the maximum speed and the reduction of speed of the spinning frame.

Therefore, an important object of the present invention is to provide improved control means for continuously and automatically regulating the speed of a spinning frame in order to obtain an optimum speed for a desired position of the build of the bobbin depending upon the tension of and/ or a particular type of yarn being wound.

Another object of the present invention is to provide an improved regulating means for pneumatically adjusting the starting or minimum speed of a spinning frame, the maximum speed, the rate of changing of speed between the minimum and maximum speed, and the reduction or retarding of speed upon reaching a maximum speed, the regulating means being simple to set to opice timum conditions for a particular yarn and/or tension and once set automatically regulating the speed throughout the build of yarn on the bobbin or the like.

Ancillary to the preceding object it is a further object of the present invention to provide a control or regulating means which will automatically reset itself when a bobbin is filled and doffed and when the ring rail lowers prior to the insertion of an empty bobbin on the spindle.

Still another object of the present invention is to provide a pneumatic drive regulator control for a spinning frame which is simple and inexpensive to manufacture, easy to adjust for a particular optimum condition and remains accurate over a long period of time and continued use of the spinning frame.

A further object of the present invention is to provide an improved sensing unit for a variable speed regulator mechanism of a spinning frame, the sensing unit operating directly off of the ring rail and sensing reciprocation as well as position of traverse of the ring rail.

Ancillary to the immediately preceding object it is a further object of the present invention to provide control means, either pneumatic or mechanical, for modifying the effect of thesensing unit, thereby controlling the starting speed, the maximum speed, and the rate of speed to the maximum speed of a spinning frame.

These and other objects and advantages of the present invention will appear more fully in the following specification, claims, and drawings in which:

FIGURE 1 is a fragmentary front elevational view of an end portion of a spinning frame, the view being somewhat schematic and showing the sensing means of the present invention;

FIGURE 2 is an enlarged schematic side elevational view, partly in cross-section and illustrating the overall regulating system of the present invention including the sensing means and the fluid actuated control means for the Reeves drive;

FIGURE 3 is an enlarged fragmentary view of the present invention illustrating the sensing means and its co-action with the ring rail of the spinning frame;

FIGURE 4 is an enlarged fragmentary end view of the ring rail and the sensing means, the pressure regulator and a portion of the sensing means being shown partly in cross-section;

FIGURE 5 is a view looking in the direction of line 5-5 in FIGURE 4 and showing the sensing wheel of the sensing means and its co-action with the operating pin of the pinion, the pinion and the rack being omitted for purposes of clarity;

FIGURE 6 is a perspective view of a modified form of the present invention applied to a spinning frame;

FIGURE 7 is a schematic view of the pneumatic control system of the modified form of invention shown in FIGURE 6;

FIGURE 8 is an enlarged side elevational view partly in cross-section of the pneumatic relay in the system shown in FIGURE 7; and

FIGURE 9 is an enlarged sectional view, partly in elevation, of the pneumatic relay shown in FIGURE 8, the view being reversed from the view of FIGURE 8.

Referring now to the drawings wherein like characters represent like or similar parts, and in particular to FIG- URES 1 and 2, the present invention is disclosed in association with a spinning frame generally designated at 10, the spinning frame being of the usual type having longitudinally extending frame members 12 and 14, a head frame member 16, a plurality of bobbin receiving spindles 18, and a vertically reciprocating and traversing ring rail 20. As is customary of spinning frames of this type used for winding filling onto bobbins, the ring rail 20 reciprocates in short strokes as yarn is being wound onto bobbins B, the ring rail being moved upwardly to a new position of traverse after a predetermined amount of yarn has been wound on the bobbin B. The progressive periodic or step by step upward traversing movement of the ring rail 20 and the reciprocation of the same in short strokes at each position of traverse builds the package on the bobbin B until the bobbin is filled and then the filled bobbin is doffed from the spindle 18 after the ring rail is lowered and an empty bobbin positioned on the spindle for a repeat operation. Usually spinning frames have a duplicate arrangement of spindles and ring rails on opposite sides of the same. This operation briefly described above is conventional for spinning frames and winding machines now utilized for filllng winding but the invention may also be used to program and regulate a frame used for warp winding.

A main drive shaft 21 of the spinning frame 10 is driven by a constant speed motor 22 having a constant speed drive shaft 24. In more detail, the main drive shaft 21 is provided with a fixed diameter sheave or pulley 26 whereas the constant speed drive shaft 24 of the motor is provided with a variable diameter pulley or sheave 28 having a fixed conical flange 30 and an opposed axially movable conical flange 32. An endless belt 34 passing about the pulleys 26 and 28 drives the pulley 26 at a speed determined by the position of the flange 32 relative the flange 30. In other words, the drive for the main shaft 21 of spinning frame is a Reeves type of drive well known in the art for varying the speed of a driven shaft from a constant speed drive shaft.

main shaft 21. The builder motion 42 rocks a cross arm 44 which in turn moves a lifting lever 46 connected to a vertically extending lifting rod 48. The lifting rod passes through a bushing 50 in the lower longitudinal frame member 14 and is fixedly attached at its upper end to the ring rail 20 and thus the ring rail is reciprocated and periodically raised during the build of the package on the bobbin in the usual manner. Each strand of yarn Y passes from a source and a guide eye not shown through the conventional traveler 52 on a ring 54 carried by the ring rail 20. The yarn Y passes inwardly from the traveler 52 to the bobbin B on which it is wound. The angle at which the yarn Y meets with the bobbin B determines the tension on the yarn and when this angle is sharp, as is the case when the inverted cone of the package is being formed, or when the yarn is being wound close to the center of package, the tension on the same is greatest and the spinning frame must be operated at its slowest speed. Conversely, as the angle of yarn to the bobbin decreases, the tension on the yarn decreases and unless the speed of the bobbin increases, the yarn balloons and is damaged when striking the guard shields between spindles. As pointed out heretofore, the purpose of the present inven-' tion is to program and accurately sense the build of a package on the bobbin so as to control the same at optimum speeds of the spinning frame accordingly so that a maximum output can be obtained from the spinning frame with a minimum damage to the yarn from ballooning. The accurate and optimum adjustment of speed of the spinning frame for a particular yarn or type of package built enables the production of a uniformly wound package.

A sensing unit generally designated at 56 senses directly the reciprocation of the ring rail 20 as well as the position of traverse of the ring rail and from this unit a fluid actuated motor 58 including a cylinder and a piston therein movable relative thereto is operated so as to control the relative position of the flange 32 with respect to the flange and thus the effective diameter of the pulley 28. This immediately varies the speed of the main shaft 21 of spinning frame 10 so as to increase or decrease the speed of rotation of spindles 18, and the reciprocation and traversing of ring rail 20. As will be discussed in more detail later in the specifications, various fine adjustments to the system may be made whereby the minimum or starting speed of the spinning frame, the maximum speed and point of reaching maximum speed on build up of the package, and the rate of change of speed between minimum and maximum speed all may be varied independently of one another or in combination with one another. It will suffice at this time to point out that optimum conditions are determined for a particular type of yarn being wound on the bobbin as well as for the type of package to be wound and when these conditions are determined, the system is adjusted accordingly and once adjusted will automatically control the speed of the spinning frame at an optimum desired speed for a particular condition of operation.

The sensing unit 56 which is best disclosed in FIG- URES 2, 3, 4, and 5 includes a pressure regulating valve means 57 operatively controlled by the position and reciprocation of the ring rail 20. In more details, the pressure regulating valve mean 57 includes a two-part housing 60 supported on the head frame 16 by a bracket 61, the housing having a diaphragm 62 therein separating a housing part 64 from a housing part 66. The part 66 is provided with an inlet fitting 68 to which is attached an inlet fluid pressure conduit 70 and an outlet fitting 72 to which is attached a fluid pressure outlet conduit 74. Housing part 66 is further provided with an inner body member 76 which divides the interior of the part 66 into an inlet pressure chamber 78 for incoming pressure fluid and an outlet pressure chamber 80 in communication with the outlet conduit 74 and one face of the diaphragm 62. Inner body member 76 provides a seat 82 for a valve element 84 biased by a spring 88 to a closed position. The valve element 84 has an axially extending stem 90 extending through the passage 91 between chambers 78 and 80, the stem 90 having its inner end conically shaped to receive a movable valve seat 92 provided about an orifice 96 in a member 94 carried by the diaphragm 62. The member 94 which has the orifice 96 extending therethrough so that it is open to both sides of the diaphragm 62 permits fluid under pressure in the chamber 80 to bleed through the orifice 96 into the chamber formed by the part 64 of the housing 60, the part 64 having an opening 98 therein whereby the fluid under pressure may further escape to atmosphere. The part 64 of housing 60 has a threaded opening 100 which is axially aligned with the valve stem 90. Threaded opening 100 is arranged to receive an externally threaded tubular stern 102. The inner end of stem 102 is arranged to engage a spring follower 104 that receives one end of a compression spring 106. The other end of the compression spring 106 abuts against the diaphragm 62 and normally biases the same in a direction opposite to the direction of biasing of the valve element 84.

Tubular stem 102 is internally threaded at 108 with a thread which is the reverse of the external threads thereon. For example, the threads 108 of stem 102 may be left hand threads Whereas the external threads 103 may be right hand threads. A shaft 110 having threads 112 thereon is threadably received within the stem 102, the shaft 110 having its innerend also capable of engaging the spring follower 104. A nylon bushing 114 is provided in the part 64 of housing 60, the nylon bushing or set screw having its inner end frictionally bearing against the external threads 103 of stem 102 for a purpose to be described later in the specification.

Ring rail 20 has attached to the end thereof an elongated vertically extending bracket or bar 116. A section of chain 118 is supported on the bracket by means of a bolt 120 at its lower end and an adjustable bolt and clamp arrangement 122 at its upper end. The chain 118 is in effect a gear rack for cooperating with a meshing pinion or gear 124 fixed to the end of the shaft 110 by means of a set screw 126. The pinion 124 has some lateral movement because of movement of the shaft 110 when threading into and out of stem 102, and therefore chain 118 is somewhat flexible so that it can accommodate for movement of the pinion. Since the housing 60 is supported on the stationary head frame 16 of the spinning frame, the reciprocation of the ring rail 20 causes the rack or chain 118 to move vertically relative to the pinion 124 meshing therewith and, thus, the pinion rotates back and forth to rock the shaft 110 about its axis causing the same to thread into and out of the stem 102. The end of the shaft 110 abutting the spring follower member 104, when the same is threaded into the housing, causes the spring follower member to increase the compression of the spring 106 which in turn moves the diaphragm 62 and valve member 94 toward the right of FIGURE 4. This movement causes the valve member 84 to lift off its seat 82 so that fluid pressure can flow into the chamber 80 and through the outlet 74 to adjust the fluid pressure to motor 58 so as to increase the speed of the spinning frame. The movement of the shaft 110 in an unthreading direction relative to the stem or sleeve 102 operates in the reverse of the above and causes a slowing down in the speed of the spinning frame due to the reduction of pressure in the chamber 80.

A sensing wheel 128 fixed to and flush with the outer end of stem 102 is provided with an under cut peripheral groove 130. A pair of circumferentially spaced radially extending pins 132 and \134 having screw heads 136 fitting into the groove 130 are carried by the sensing wheel 128 in a desired adjusted position. The radially extending pins 132 and 134 cooperate with a pin 138 extending from the pinion or gear 124 parallel to and spaced from its axis. When the ring rail 20 changes its position of traverse vertically, i.e. the ring rail moves upwardly to a new position where it reciprocates, the pin 138 will engage the pin 134 on the sensing wheel 128 and cause the sensing wheel to rotate a small increment. When this occurs the tubular stem 102 is threaded inwardly of the housing 60 to a new position and further increases the load on the spring 106 so a to move the diaphragm62 to a new position toward the right of FIGURE 4. This will cause the valve member 84 to open further and increase the pressure of fluid in the chamber 80 and to the fluid actuated motor 58 so that the overall speed of the spinning frame is increased. While the ring rail is reciprocating at this new position of traverse, the stem 102 is frictionally retained in its relative position to the housing 60 by means of the nylon set screw 114 and thus the rocking of the pinion 124 by the reciprocation of the ring rail merely causes the shaft 110 to thread in and out of the stem to vary the speed of the spinning frame relative to the new overall speed of the spinning frame at this position of traverse of the same. The only time the pin 134 of the pinion 124 is engaged by the pin 138 is when the builder motion unit 42 causes the ring rail to move to a new position of traverse.

When the bobbin B has been filled and the package is completed, the ring rail 20 is then lowered by the builder motion unit 42 to the lowermost starting position and when this occurs the pin 138 engages the pin 132 on the sensing wheel 128 to rotate the same in the opposite direction to thereby reset the stern 102 to a predetermined overall minimum starting speed. The filled bobbin is then doffed and an empty bobbin is placed on the spindle.

Referring now to FIGURE 2, it will be noted that the movable flange 32 is provided with a hub 138 keyed to the constant speed shaft 24. Hub 138' is provided with a groove in its periphery in which a thrust collar 140 rides, the thrust collar having radially extending pins 142. The pins 142 are received in slots 144 provided in levers 146, the levers 146 being pivoted at one end to a bracket 148 extending upwardly from a motor base plate 150. A fixed standard or guide rod 152 also extends upwardly from the motor base plate 150 and is provided at its upper end with a bushing 154. A connecting rod 156 slidable in the bushing 154 has one end threaded as indicated at 158 and the other end provided with a yoke 160. A pin 162 extending through the yoke also extends through a slot 164 in a link 166 pivoted at 168 to a second link 170, the second link being pivotally supported on the standard 152 as indicated at 172. A pivot block 174 having pins 176 extending therefrom is adjustably supported on the threaded end 158 of the connecting rod 156 by means of the jam nuts 178 and 180. Pins 176 ride in slots 182 in the free ends of the levers 146. A stop nut 184 is positioned between the pivot block 174 and the standard 152 and determines how far the levers 146 can be moved clockwise as viewed in FIGURE 2 and thus controls the maximum speed of the spinning frame. On the other end, the jam nuts 178 and adjustably support the pivot block 174 on the connecting rod 156 and thus determine the minimum or starting speed of the spinning frame when the ring rail 20 is at its lowermost position of traverse.

The fluid actuated motor 58 which is connected to the sensing unit 56 by means of the fluid conduit 72 includes a two-part housing 186 and a movable cup-shaped piston 188. Interposed between the cup-shaped piston 188 and the housing 186 is a flexible diaphragm 190. Cup-shaped piston 188 is provided with a piston block 192 having a piston rod 194 extending axially thereof through a. sleeve 196 at one end of the housing 186. The outer end of the piston rod is provided with a bifurcated member 198 pivotally connected to the link 166 as indicated at 200. The sleeve 196 is exteriorly threaded and is provided with an adjustment nut 202. A compression spring 204 interposed between the adjustment nut 202 and the piston block 192 applies a predetermined load on the diaphragm, this load being adjustably varied by changing the position of the nut 202 on the sleeve 196.

Pressure conduit 72 is provided with a pressure gauge 206 for indicating the operating pressures of the fluid pressure actuated motor 58. By knowing a desired starting speed for the spinning frame and the pressure required on the motor 58 necessary to obtain this speed, ad-

justment for the same can be made to the system by use of the nuts 178 and 180. To obtain a slower speed the nut 178 is loosened whereas nut 180 is tightened so as to shift the relative position of the pivot block 174 to the left of FIGURE 2. Likewise, the position of the nut 184 can be adjusted so that the maximum speed of the spinning frame can be obtained at any point on the build up of the bobbin.

Compressed air is used to motivate the motor 58 through the pressure regulating sensing unit 56 but it is, of course, within the scope of the present invention to utilize other fluids under pressure, such as water, oil, or the like.

The operation of the system for controlling the speed of a spinning frame may be described briefly as follows: Beginning at the lower end of an empty bobbin B on spindle 18, the yarn Y is wound on the same in an inverted cone. Knowing the type of yarn and the tension which such yarn can take, the minimum speed of the main shaft 21 is adjusted by adjusting the nuts 178 and 180. Knowing the type of package to be formed and the point on such package when a maximum speed is desired to be reached, then an adjustment is made for obtaining this maximum speed at this point by changing the position of the adjusting nut 184. Once this has been set, then the spinning frame is ready for operation in winding bobbins with the particular yarn desired.

As the yarn begins to wind onto the bobbin B when forming the inverted cone, the spinning frame is operated at a desired substantially constant overall minimum speed which is sensed by the ring rail reciprocating at its lowermost position of traverse. The package begins to build on 'the bobbin B with the inverted cone being formed first.

During this portion of the build, the reciprocation of the ring rail does not effect a speed change due to the adjustment of the system. However, when the package has been built about one quarter of the way up the bobbin, the inverted cone will have been completed and a partial upright cone is built during reciprocation of the ring rail at this particular position of traverse. This continues as the package is completed with a differential of speed being maintained at each position of traverse for each change in overall speed. The ring rail will make short vertical strokes at each point of traverse and consequently the stem 102 will not rotate but the shaft 110 will rock on its axis due to the rotation back and forth of the pinion 124 in one direction and another depending on the direction of reciprocation. As the ring rail 20 is on its upward stroke, the pinion 124 is rotated in a direction to cause shaft 110 to move to the left of FIGURE 4 and thus disengage the spring follower 104 from spring 106 to relieve pressure of the spring 106 on the diaphragm 62. This will cause the valve member 94 to move its seat 92 slightly off of the conical end of the valve stem 90 and air pressure in the chamber 80 starts to bleed to atmosphere, reducing the pressure in the conduit 74 to the air motor 58. When the pressure behind the diaphragm 190 of the air motor is reduced the compression spring 204 of the air motor urges the cup-shaped piston 188 to the left which in turn will cause the link 166 to move the connecting rod 156 to the left. When the connecting rod 156 moves to the left it, of course, causes the lever 146 to pivot counterclockwise as viewed in FIGURE 2 thus causing the movable flange 32 to move away from the fixed flange 30 thereby reducing the effective diameter of the pulley 28 which in turn reduces the speed of the main shaft 21 of the spinning frame. This reduction in speed occurs as the yarn approaches the bobbin when the upright cone is being made.

The reverse procedure occurs when the ring rail 20 is on its lower stroke and angle of the yarn decreases with respect to the traveler. When the ring rail 20 is on its downward stroke it causes the pinion 124 to rotate in a direction to move the shaft 110 to the right of FIGURE 4 and thus the shaft engages the spring follower 104 and increases the pressure of the spring on the diaphragm 62. This closes the orifice 92 and moves the valve stem 90 to the right permitting more fluid under pressure to enter the chamber 80 and thereby increase the pressure to the air motor 58. It will be understood that the overall speed at a position of traverse for the reciprocating n'ng rail 20 is determined by the position of the stem 102 relative the housing 60. When the ring rail 20 moves upwardly to a new position of build up or traverse as by the build up unit, the initial upward stroke of the ring rail is greater than the strokes of the ring rail at the old position of traverse. Consequently, the rotation of the pinion 124 to a greater extent causes the pinions operator pin 138 to engage the pin 134 on the sensing wheel 128 thus rotating the sensing wheel and its stem 102 in a direction to advance the stern into the housing 60 and thus apply additional pressure on the spring 106. This permits the valve 84 to move off of its seat a greater distance allowing more pressure to build up in the chamber 80 before this pressure is effective and the diaphragm, and thus the pressure line 74 to the air motor 58 is increased whereby the cup-shaped piston of the air motor 58 is moved further to the right of FIGURE 2 so as to further increase the overall speed. When this overall speed has been increased, then the reciprocation of the ring rail at this new position functions as described above and varies the spinning frames speed relative to this new overall speed.

The procedure of increasing the overall speed when the ring rail 20 moves to a new position of traverse continues throughout the build up on the bobbin until such time that the nut 184 on connecting rod 156 engages the standard 152. Then a maximum speed for a particular condition is reached and the reciprocation of the ring rail merely varies the speed of the spinning frame slightly with respect to this maximum speed for the remainder of 8 the build up of the bobbin until the bobbin is filled and doffed.

After the bobbin is filled, the ring rail 20 is lowered by the build up unit 42 to its lowermost position of traverse and the bobbin is doifed. As the ring rail 20 is being lowered, the pinion 124 is rotating in a direction to cause its operating pin 138 to engage the pin 132 and rotate the sensing wheel 128 in a reverse direction to that described above. This causes the stem 102 to withdraw from the housing 60 a predetermined distance thus relieving the additional pressure applied to the compression spring 106 and diaphragm 62 so as to reset the sensing unit for the start of a new cycle. An empty bobbin B is then placed on the spindle 18 and the cycle is repeated.

Referring now to FIGURES 6 through 9 inclusive, there is disclosed a modification of the control system just previously described, the modification including primarily the provision of pneumatic means coupled with the sensing unit of the present invention for adjusting the minimum and/or maximum speed of the spinning frame, and the rate of speed change of the spinning frame between the minimum or starting speed and the maximum speed. In FIGURES 6 to 9 elements or members which are substantially identical with those previously described are given the same reference numerals.

The overall modified system is best disclosed by referring specifically to FIGURES 6 and 7. It will be noted that a fluid pressure inlet conduit 210 leading from a suitable source of compressed air (not shown) is con nected to an air manifold conduit 212. The inlet conduit 210 may be provided with a pressure gauge 214 for indicating the inlet air pressure to the system. Manifold 212 has a plurality of pressure lines leading therefrom to various control units for the system. In more detail, a fluid pressure inlet conduit 216 having a manually operable pressure regulator 218 therein extends from the manifold 212 to the pressure regulating valve means in housing 60 of the sensing unit 56. A fluid pressure outlet conduit 220 extends from the pressure regulating valve means of the sensing unit 56 to a fluid pressure or air relay valve generally designated at 222 which will be described in more detail later in the specification. A second fluid pressure conduit 224 also having a manually controllable pressure regulator 226 therein extends from manifold 212 directly to the fluid pressure or air relay 222. A third fluid pressure conduit 228 having a manually controlled pressure regulator 230 therein extends from the manifold 212 to an air cylinder 232 mounted by means of a clamp 233 on a lever 234 pivotally connected to the outside of a body or casing 236 of the air relay 222 as indicated at 238. The conduit 228 is flexible as the cylinder 232 to which it is attached must be capable of pivoting with the lever 234 as will be explained in more detail later in the specification. A third fluid pressure conduit 240 having a manually controlled pressure regulator 242 therein extends from the manifold 212 to an auxiliary air cylinder 244, the conduit 240 also being flexible as the air cylinder 244 is movable as will be explained in more detail later in the specification. A fourth fluid pressure conduit 246 having a man: ually operable pressure regulator 248 therein extends from the manifold 212 to the air relay 222.

Additionally, it will be noted that the air relay 222 has a conduit 250 extending therefrom to the air motor 58 and variable pressure supplied through the conduit 250 from the air relay 222 controls the actuation of the air motor 58, and, more particularly, the movement of its piston rod 194 in a manner substantially identical to that described above with respect to the system disclosed in FIGURES l to 5 inclusive. Air motor 58 in FIG- URES 6 and 7 may be operatively connected to the movable flange 32 of the pulley or sheave 28 by a linkage arrangement substantially identical to that disclosed in and described relative to FIGURES 1 and 2.

Referring now specifically to FIGURE 9, it will be noted that the body member or casing 236 of the air relay 222 is provided with a first chamber 252 separated into an upper chamber 254 and a lower chamber 256 by a double diaphragm unit 260 which supports centrally thereof a movable member 262. The double diaphragm unit 260 is in effect a pair of diaphragms 264 and 266 having their outer surfaces exposed to fluid pressure in the respective chambers 256 and 254. Conduit 220 extending from the pressure regulating valve means 57 of the sensing unit 56 is connected to a fitting 268 received in a passage 269 leading to the lower chamber 256 and thus air under pressure from the sensing unit 56 acts on the lower surface of diaphragm 264 to urge the double diaphragm unit 260 and its member 262 upwardly as viewed in FIGURE 9. A spring 270 between the member 262 and a lower wall 272 of chamber 256 normally biases the member 262 in an upward direction and provides a predetermined static load on the diaphragm unit 260.

The member 262 is provided in its upper surface with a Well or closed bottom bore 274 having a valve seat 276 in the upper portion thereof for cooperating with a ball valve element 278. Communicating with the well or bore 274 intermediate the spaced diaphragms 264 and 266 of the diaphragm unit 260 is a vent passage 280 leading to atmosphere. The purpose of the vent passage 280 will be described more fully later in the specification.

The upper chamber 254 communicates with a counter bore 282 in the body or casing 236 by means of a passage 290. The ends of the passage 290 are provided with valve seats 292 and 294, respectively. Counter bore 282 has a ball valve 296 therein normally biased by spring 298 toward the valve seat 294 whereas the valve seat 292 is arranged to cooperate with the ball valve 278 under certain conditions of operation. Also, intermediate the ball valves 278 and 296 and extending through the passage 290 is a losely fit push pin 300, the pin being arranged to lift ball valve 296 off its seat when ball valve 278 is raised by member 262. Counter bore 282 communicates by a passage 302 with a fitting 304 to which is attached the fluid pressure conduit 246. Conduit 250 extending to the air motor 58 is connected to a fitting 306 and communicates by means of a passage 308 to the pressure chamber 254. The upper portion of the body member or casing 236 of air relay 222 is provided with a well 310 having a diaphragm 312 therein spaced from a second diaphragm 314, the latter being held in position by a cover plate 318. The space between the diaphragms 312 and 314 defines a pressure chamber 316 which is in communication with the fluid pressure conduit 224 by means of a passage 320 and a fitting 322. Diaphragm 312 supports a plate member 324 movable therewith, the plate member hav ing an upstanding projection or pin 326 thereon. The plate member 324 is bolted to the movable member 262 by means of spacer bolts or studs 328 extending through bolt holes 330 in the casing 236. By such an arrangement it will now be apparent that movement of either the plate 324 or the movable member 262 causes a corresponding movement of the other of the two elements. The upper diaphragm 314 supports a projection or pin 332 extending through a hole 334 in cover plate 318.

A lever 336 pivotally connected as indicated at 340 to ears 338 on cover plate 318 bears against the upper end of the pin 332. The lever 336 is provided with a cam surface 342, the purpose of which will be described later in the specification.

Referring now to FIGURE 8, it will be noted that the air cylinder 232 is provided with a piston 344 normally biased by spring 346 toward the opening of the conduit 228 into the cylinder. The piston 344 has a piston rod 343 extending from the end of the cylinder 232, the piston rod 348 being operatively connected to a pin 350 extending through an elongated slot 352 in the lever 234. Pin 350 cooperates with the cam surface 342 at different points 10 therealong depending upon the extension of the piston rod 348 caused by the pressure within the cylinder 332.

Referring now back to FIGURES 6 and 7, it will be noted that the piston rod 194 of the air motor 58 has a plate element 352 attached thereto by nut 354 and movable therewith. One end of the plate element 352 is rigidly attached to a piston rod 356 of the auxiliary air cylinder 244. The piston rod 356 is provided with a piston 358 which in turn is spring urged by compression spring 360 toward the right of FIGURE 7 and in a direction opposing air pressure behind the piston. The free end of auxiliary air cylinder 244 is supported by a spring 362 attached thereto and extending to and connected with the end of lever 234. The tension of spring 362 on the lever 234 is in a direction which urges the lever about its pivot 238 so that the pin 350 is urged into engagement with the cam surface 342 of the lever 336. As will now be apparent the mounting of the cylinder 244 between the lever 234 and plate member 352 is such that the cylinder is free to move relative the piston 358 or the piston is free to move relative the cylinder. 7

The operation of the system disclosed in FIGURES 6 to 9, inclusive, may be described briefly as follows: It will be understood that the sensing unit 56 of the system of FIGURES 6 to 9 operates identically with that previously described with respect to the system of FIGURES 1 to 5 in that it senses the reciprocation of the ring rail 20 and/or of the position of traverse of the ring rail as the package is being built on the bobbin B and regulates the pressure of air supplied therefrom. The sensing unit of the modified form of the invention is supplied with air under pressure through the conduit 216 and regulates the amount of air under pressure delivered by the outlet conduit 220 to the air relay 222. The variation of pressure in the conduit 220 is reflected on the diaphragm unit 260 and, more particularly, pressure exposed on the surface of the diaphragm 264.

Before describing the control of the diaphragm unit 260 by changes in pressure in the conduit 220 as sensed by the sensing unit 56, it will be best to describe the operation of the various pneumatic controls for effecting the optimum starting speed of the spinning frame, the optimum maximum speed of the spinning frame, and the optimum rate of change of speed between the starting or slow speed and the maximum speed of the spinning frame. The operator, knowing the particular type of yarn to be wound on the bobbin and the characteristics of such yarn will first set the control system up so that the spinning frame operates at an optimum starting or minimum speed for the Winding of this particular yarn in a particular type of package. This is accomplished by adjusting the manually adjustable pressure regulator 226 in the conduit 224 so that air under a predetermined selected pressure is supplied by the conduit 224 to the pressure chamber 316 of the air relay 222. This pressure of air acts on the diaphragm 212 and effectively opposes the movement upwardly of the diaphragm unit 260 by the spring 270 and air pressure supplied to the chamber 256 from the sensing unit. In other words, the diaphragm unit 260 is provided with a predetermined load opposing its change of position by fluid under pressure entering into the chamber 256.

Once the minimum speed control has been adjusted by regulating the manually controlled pressure regulator 226, then the operator adjusts the manually controlled pressure regulator 242 to supply fluid under predetermined pressure to the auxiliary cylinder 244. The pressure entering the cylinder 244 acts on the piston 358 tending to move the same against the spring 360. The piston rod thus adds tension on the spring 204 of the air motor 58 which resists movement of the cup-shapedpiston and its piston rod toward the right of FIGURE 7. In other words, this adjustment limits the maximum speed of the spinning frame It) at a predetermined position of build by the ring rail 20 based on the pressure supplied by the sensing unit 56 when applied to the chamber 256.

The manually adjustable pressure regulator 230 is selectively set to supply air to the cylinder 232 at a predetermined pressure and this moves or urges the piston 344 to a predetermined position whereby the pin 358 of piston rod 348 rides to a certain position on the cam 342. When the piston rod 348 is moved to the right of FIGURE 9 and the pin rides up the cam 342, it causes the lever 336 to pivot counterclockwise about its pivot 340 which in turn urges the pin 332 downwardly to a position where it engages the pin 326 and thus moves the diaphragm 312 as well as the diaphragm unit 260 downwardly. By regulating the pressure through the pressure regulator 230 the rate of change of speed of the spinning frame between the selected starting or slow speed and the selected maximum speed is controlled.

Fluid pressure for actuating the air motor 53 in response to the various controls discussed above is controlled by the manually operable pressure regulator 248. This regulator is selectively set to a predetermined optimum operating condition and a predetermined pressure of thefluid supplied through conduit 246 to the counter bore 282 is maintained. When the operation of the spinning frame has been set up as above and when the sensing unit applies fluid to the line 220 under an increased pressure, this will cause the diaphragm unit 260 to move upwardly, carrying with it the movable member 262 and the ball valve 273. The ball valve 278 moves the pusher pin 300 upwardly to unseat the ball 296 and fluid under pressure from the chamber or counter bore 282 can flow downwardly through the passage 2% and out into the chamber 252. From the chamber 252, the fluid under pressure flows through the line 250 to the air motor 58 to actuate the piston therein thus increasing the speed of the spinning frame. When the sensing unit reduces the pressure in the line 229, the reverse occurs in that the pressure in chamber 256 decreases and the pressure acting on the diaphragm 266 moves the diaphragm unit 260 downwardly to a point where the ball valve 278 unseats from its seat 276 so that pressure can bleed from the chamber 254 to atmosphere through the passage 280 thus reducing the pressure in the line 250 to the air motor 58. Of course, it will be understood that the static pressures adjustably controlled in the air cylinders 232 and 244 as well as the static pressure of air in the chamber 316 also adjustably controlled, effect or modify the overall operation as described above.

By changing any of these static pressures through adjustment of the respective pressure regulators 226, 230, and 242, one or more of the conditions of operation are changed. For example, if it is desired to increase the maximum speed of the spinning frame, pressure is reduced in the cylinder 244 so that the piston rod 194 can move further to the right of FIGURE 7 for the same amount of pressure previously applied through the pressure chamber 252 as controlled by the sensing unit 56. Likewise, if the starting speed or maximum speed is desired to be decreased, then the pressure in chamber 316 is decreased so that the static load on the diaphragm 312 is reduced thus permitting air at a predetermined pressure in chamber 256 to lift the diaphragm unit 260 more easily. The control for the rate of change of speed between minimum and maximum speed of the spinning frame can be easily adjusted by changing the air pressure in the cylinder 232 to move the piston rod 348 one way or the other to change the relative position of the pin 350 on the cam 342.

The control system and sensing unit of the present invention heretofore described and illustrated in the drawings fully and effectively accomplishes the objects and advantages of the present invention. It will be realized, however, that the foregoing specific embodiments have been shown and described only for the purposes of illus trating the principles of this invention and are subject to some changes without departing from such principles or the spirit of the invention. Therefore, the terminology used throughout the specification is for the purpose of description, and not limitation, the spirit and scope of the invention being defined in the appended claims.

What is claimed is:

1. In a winding machine having at least one spindle, a reciprocating ring rail, a main shaft to rotate said spindle and reciprocate said ring rail, a constant speed shaft, drive means operatively connecting said main shaft to said constant speed shaft, and fluid pressure actuated means for varying the speed at which said drive means drives said main shaft: the improvement in means for controlling said fluid pressure actuated means comprising a conduit extending from a source of fluid under pressure, a pressure regulating valve means, said pressure regulating valve being connected to said conduit, a second conduit extending from said pressure regulating valve means to said fluid pressure actuated means, and sensing means directly connected to said ring rail and to said pressure regulating valve means for sensing position of and reciprocating movement of said ring rail, said sensing means controlling said pressure regulating valve means in accordance with the condition sensed without a lag.

2. In a winding machine having at least one spindle, a reciprocating and traversing ring rail, a main shaft to rotate said spindle and reciprocate said ring rail and cause the same to traverse a constant speed shaft, drive means operatively connecting said main shaft to said constant speed shaft, and fluid pressure actuated means for varying the speed at which said drive means drives said main shaft: the improvement in means for controlling said fluid pressure actuated means comprising a conduit extending from a source of fluid under pressure, a pressure regulating valve means, said pressure regulating valve means being connected to said conduit, a second conduit extending from said pressure regulating valve means to said fluid pressure actuated means, and sensing means directly connected to said ring rail and said pressure regulating valve means for sensing without lag the position of and reciprocating movement of said ring rail, said lastmentioned means including a first means operable in response to reciprocation of said ring rail for selectively opening and closing said valve means to increase and decrease the speed of said main shaft, and a second means operatively connected to said first means and responsive to a change in position of said ring rail for controlling said valve means to increase overall speed of said main shaft.

3. A structure as claimed in claim 2 including means for controlling maximum speed of said mainshaft at a predetermined position of the traverse of said ring rail.

4. The structure as claimed in claim 2 in which said first means includes a rack carried by said ring rail, a pinion engaging said rack and rotatable upon movement of the same, a shaft carried and moved by said pinion and operatively connected to said pressure regulating valve means for controlling the same upon movement of said pinion.

5. A structure as claimed in claim 4- in which said second means includes a sensing wheel, means operatively connected to said ring rail for rotating said sensing wheel a predetermined amount upon a change in position of said ring rail, and a stem carried and movable by said sensing wheel, said stem being operatively connected to said pressure regulating valve for controlling the same to increase overall speed of said main shaft during variation of speed of said main shaft by the reciprocation of said ring rail.

6. In a winding machine having at least one spindle, a reciprocating and traversing ring rail, a main shaft to rotate said spindle and reciprocate said ring rail and cause the same to traverse, a constant speed shaft, variable drive means operatively connecting said main shaft to said constant speed shaft: the improvement comprising a fluid actuated motor including an air cylinder and a piston movable therein and operatively connected to said variable drive means for changing the speed of the main shaft; a sensing means including a pressure regulating valve means connected directly to said ring rail and means for controlling said pressure regulating valve means in response to reciprocation and position of traverse of said ring rail without lag; a first conduit extending from a source of pressure to said sensing means; and a second conduit extending from said pressure regulating valve means and operatively connected said fluid motor for controlling fluid under pressure thereto to move the piston therein.

7. A structure as claimed in claim 6 in which said pressure regulating valve means includes a housing, an inlet valve in said housing biased in one direction, a diaphragm in said housing movable to open said inlet valve and responsive to fluid pressure when said inlet valve is open, means for biasing said diaphragm in a direction opposite the direction of biasing of said inlet valve, a bleed valve through said diaphragm and operable by position of said diaphragm, and in which said control means for said pressure regulating valve means including a first means operable in response to a position of traverse of said ring rail for modifying the biasing means on said diaphragm to control overall speed of said main shaft, and a second means operable in response to reciprocation of said ring rail at the position of traverse to modify said biasing means subject to the modification by said first means.

8. A structure as claimed in claim 7 including means to limit maximum speed of said main shaft.

9. A structure as claimed in claim 8 in which said last-mentioned means includes a mechanical stop for operatively controlling the maximum movement of the piston of the cylinder of said fluid actuated motor.

10. A structure as claimed in claim 8 in which said last-mentioned means includes an auxiliary fluid actuated cylinder having a piston therein operatively connected to the piston of said fluid actuated motor, and means to supply fluid at a predetermined pressure to said auxiliary fluid actuated cylinder.

11. A structure as claimed in claim 8 including means to limit minimum speed of said main shaft.

12. A structure as claimed in claim 11 in which said minimum speed limiting means includes a mechanical stop for operatively controlling the position of the piston of the cylinder of said fluid actuated motor relative the variable drive means.

13. A structure as claimed in claim 11 in which said minimum speed controlling means includes a fluid pressure relay connected to said second conduit and operable by pressure from said pressure regulating valve means, said fluid pressure relay having an inlet for a source of fluid pressure, an outlet connected to said fluid actuated motor, valve means interposed between said inlet and outlet, diaphragm means responsive to pressure from said pressure regulating valve means for opening the valve means in said relay, a second diaphragm means operatively connected to said first diaphragm means, means for applying fluid under pressure to said second diaphragm means to oppose action of said first diaphragm means and control the minimum speed of said main shaft and a third diaphragm means operatively associated with said second diaphragm means to apply a predetermined load thereto whereby the rate of speed of the main shaft is controlled, a pivoted lever operatively connected to said third diaphragm means for actuating the same, an air cylinder operatively connected to said lever for applying a predetermined force on the same, and a source of fluid pressure for said last-mentioned fluid pressure cylinder.

14. A structure as claimed in claim 13 in which said means to limit maximum speed of said main shaft includes an auxiliary fluid actuated cylinder having a piston therein operatively connected to the piston in said fluid actuated motor, means to supply fluid at a predetermined pressure to said auxiliary fluid actuated cylinder, and spring means operatively connecting one end of said auxiliary fluid actuated cylinder to the end of said lever.

15. A structure as claimed in claim 6 in which said pressure regulating valve means includes a housing, an inlet valve in said housing biased in one direction, a diaphragm in said housing movable to open said inlet valve and responsive to fluid pressure when said inlet valve is open, means for biasing said diaphragm in a direction opposite the biasing of said inlet valve, a bleed valve through said diaphragm and operable by position of said diaphragm, and in which said control means for said pressure regulating valve means includes a tubular stem having exterior threads in one direction and interior threads in an opposite direction, said stem being threadably received in said housing and engaging said biasing means for said diaphragm, a sensing wheel carried on the outer end of said stem, a pinion rotatable on the same axis as the axis of said stern, a rack carried by the ring rail and engaging said pinion, means on said pinion for progressively rotating said sensing wheel as the ring rail changes its position of traverse, a threaded shaft carried by said pinion and threadably received within said stern, said threaded shaft having its inner end operatively engaging the biasing means of the diaphragm of said pressure regulating means.

16. A structure as claimed in claim 15 in which said sensing Wheel is provided with a peripheral under cut groove, a pair of radially extending pins adjustably secured in the groove in said sensing wheel, said pinion having an axially extending pin for cooperating with the pair of radially extending pins in said sen-sing wheel.

17. A structure as claimed in claim 16 including friction means in said housing engaging the exterior threads of said stem for frictionally holding said stem in an adjusted position.

18. A structure as claimed in claim 17 in which said friction means includes a nylon bushing extending through said housing and bearing against the exterior threads of said stem.

References Cited UNITED STATES PATENTS 1,926,390 9/1933 Kooistra 242-26.1 X 2,122,434 7/1938 Morton 242-26.1 2,503,099 4/1950 Culbreath 57-54 2,575,031 11/1951 Smith 242-261 2,587,897 3/ 1952 Rayfield 57-95 2,803,107 8/1957 Long 57-95 2,918,779 12/1959 Long 57-98 2,996,870 8/ 1961 Fornes et al. 57-95 3,015,203 1/1962 Heiberg 57-98 X 3,015,204 1/1962 Long 57-98 3,075,342 1/ 1963 Lohest et al. 57-54 FRANK I COHEN, Primary Examiner.

A. J. SIDOTI, Assistant Examiner. 

1. IN A WINDING MACHINE HAVING AT LEAST ONE SPINDLE, A RECIPROCATING RING RAIL, A MAIN SHAFT TO ROTATE SAID SPINDLE AND RECIPROCATE SAID RING RAIL, A CONSTANT SPEED SHAFT, DRIVE MEANS OPERATIVELY CONNECTING SAID MAIN SHAFT TO SAID CONSTANT SPEED SHAFT, AND FLUID PRESSURE ACTUATED MEANS FOR VARYING THE SPEED AT WHICH SAID DRIVE MEANS DRIVES SAID MAIN SHAFT: THE IMPROVEMENT IN MEANS FOR CONTROLLING SAID FLUID PRESSURE ACTUATED MEANS COMPRISING A CONDUIT EXTENDING FROM A SOURCE OF FLUID UNDER PRESSURE, A PRESSURE REGULATING VALVE MEANS, SAID PRESSURE REGULATING VALVE BEING CONNECTED TO SAID CONDUIT, A SECOND CON- 